Hybrid drive device

ABSTRACT

A hybrid drive device includes: a rotor; a transmission; and a case, in which a rotor support member that supports a rotor of the rotary electric machine includes an annular member that faces an end wall portion of the case, the end wall portion includes a first tubular portion that protrudes in an axial direction from an inner periphery toward the transmission, and a second tubular portion that protrudes in the axial direction toward the transmission so as to surround the first tubular portion, the annular member includes a tubular portion that protrudes in the axial direction from an inner periphery toward an engine, an inner side radial bearing is disposed between the first transmitting shaft and an inner peripheral surface of the first tubular portion of the end wall portion, a clearance is formed between an outer peripheral surface of the first tubular portion of the end wall portion and an inner peripheral surface of the tubular portion of the annular member, and an outer side radial bearing is disposed between an outer peripheral surface of the tubular portion of the annular member and an inner peripheral surface of the second tubular portion of the end wall portion. As a result, the durability of the bearing for supporting the rotor of the rotary electric machine in the radial direction can be further improved.

TECHNICAL FIELD

The present disclosure relates to a hybrid drive device including anengine, a rotary electric machine, a transmission coupled to the rotaryelectric machine, and a clutch that couples the engine and the rotaryelectric machine and that releases the connection of the two.

BACKGROUND ART

Conventionally, as a hybrid drive device of this type, a hybrid drivedevice including a case for housing a rotary electric machine and aclutch, and a rotor support member that supports a rotor and that isrotatably supported by the case is known (for example, see PatentDocuments 1). The case of this hybrid drive device includes a supportwall portion extending in a radial direction on the engine side, and anannular boss portion that protrudes in an axial direction toward thetransmission is formed in an inner peripheral portion of the supportwall portion. An annular plate-shaped member is fixed to the rotorsupport member so as to face the support wall portion, and a tubularportion protruding in the axial direction toward the engine is formed onan inner periphery of the plate-shaped member. Further, a ball bearingis disposed between an inner peripheral surface of the boss portion ofthe support wall portion and an outer peripheral surface of the tubularportion of the plate-shaped member. As a result, the rotor supportmember, that is, the rotor of the rotary electric machine is rotatablysupported and supported in the radial direction by the case via the ballbearing. Further, a radial bearing is disposed between an innerperipheral surface of the tubular portion of the plate-shaped member andan outer peripheral surface of an input member driven by the engine. Asa result, the input member is rotatably supported and supported in theradial direction by the case via the ball bearing, the tubular portionof the plate-shaped member, and the radial bearing.

RELATED ART DOCUMENTS Patent Documents

-   Patent Document 1: Japanese Unexamined Patent Application    Publication No. 2017-177884 (JP 2017-177884 A)

SUMMARY OF THE DISCLOSURE Problem to be Solved by the Disclosure

In the conventional hybrid drive device described above, a deflectionwith respect to the axis of a crankshaft is generated in accordance witha rotation of the engine and transmitted to the input member describedabove. Thus, the input member also deflects with respect to the axis,and the deflection of the input member is transmitted to the ballbearing via the radial bearing and the tubular portion of theplate-shaped member. Further, in the hybrid drive device describedabove, one of an inner race and an outer race of the ball bearing ispress-fitted into the support wall portion of the case or the tubularportion of the plate-shaped member, and the other is press-fitted intothe tubular portion of the plate-shaped member or the support wallportion of the case. Thus, in the hybrid drive device described above,wear may occur at a fitting portion of the ball bearing and theplate-shaped member or the case due to the deflection of the inputmember, and the rotor support member may not be appropriately supportedby the case. Further, since the deflection of the input member istransmitted to the ball bearing, the increase in the load may lead to anincrease in the size of the ball bearing.

Therefore, it is a main object of the present disclosure toappropriately support the rotor of the rotary electric machine of thehybrid drive device and to reduce the size of the bearing for supportingthe rotor in the radial direction.

Means for Solving the Problem

A hybrid drive device of the present disclosure includes a rotaryelectric machine having a stator and a rotor, a transmission coupled tothe rotary electric machine, a clutch that couples an engine and therotary electric machine and that releases connection of the two, and acase for housing the rotary electric machine and the clutch, and thehybrid drive device includes: a first transmitting shaft coupled to anoutput shaft of the engine; a second transmitting shaft that transmitspower from the rotor of the rotary electric machine to the transmission;and a rotor support member that supports the rotor of the rotaryelectric machine, in which the case includes an end wall portion that isextended so as to face the rotary electric machine and the clutch on theengine side, the rotor support member includes an annular member that isdisposed so as to face the end wall portion of the case, the end wallportion includes a first tubular portion that protrudes in an axialdirection from an inner periphery toward the transmission, and a secondtubular portion that protrudes in the axial direction toward thetransmission so as to surround the first tubular portion, the annularmember includes a tubular portion that protrudes in the axial directionfrom an inner periphery toward the engine, an inner side radial bearingis disposed between the first transmitting shaft and an inner peripheralsurface of the first tubular portion of the end wall portion, aclearance is formed between an outer peripheral surface of the firsttubular portion of the end wall portion and an inner peripheral surfaceof the tubular portion of the annular member, and an outer side radialbearing is disposed between an outer peripheral surface of the tubularportion of the annular member and an inner peripheral surface of thesecond tubular portion of the end wall portion.

In the hybrid drive device of the present disclosure, the case includesthe end wall portion that is extended so as to face the rotary electricmachine and the clutch on the engine side, the rotor support memberincludes the annular member that faces the end wall portion of the case.The end wall portion of the case includes the first tubular portion thatprotrudes in the axial direction from the inner periphery toward thetransmission, and the second tubular portion that protrudes in the axialdirection toward the transmission so as to surround the first tubularportion, and the annular member described above includes the tubularportion that protrudes in the axial direction from the inner peripherytoward the engine. The inner side radial bearing that supports the firsttransmitting shaft in the radial direction is disposed between the firsttransmitting shaft that is coupled to the output shaft of the engine andthe inner peripheral surface of the first tubular portion of the endwall portion, the clearance is formed between the outer peripheralsurface of the first tubular portion and the inner peripheral surface ofthe tubular portion of the annular member. The outer side radial bearingfor supporting the rotor support member in the radial direction isdisposed between the outer peripheral surface of the tubular portion ofthe annular member and the inner peripheral surface of the secondtubular portion of the end wall portion. Thus, even if deflection of thefirst transmitting shaft with respect to the shaft center occurs inaccordance with the rotation of the engine, since the clearance isformed between the outer peripheral surface of the first tubular portionand the inner peripheral surface of the tubular portion of the annularmember, the deflection of the first transmitting shaft does not affectthe tubular portion of the annular member. Thus, in the hybrid drivedevice of the present disclosure, the rotor support member can beproperly supported by the case via the outer side radial bearing.Further, since the first transmitting shaft is supported in the radialdirection by the end wall portion of the case via the inner side radialbearing, a torque fluctuation (vibration) of the engine transmitted tothe first transmitting shaft is no longer directly transmitted to theouter side radial bearing. As a result, in the hybrid drive device ofthe present disclosure, the load acting on the outer side radial bearingfor supporting the rotor support member, that is, the rotor of therotary electric machine in the radial direction can be decreased, thedurability thereof can be further improved, and the outer side radialbearing can be decreased in size (the cost can be decreased).

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic configuration diagram showing a hybrid drivedevice including a case of a rotary electric machine of the presentdisclosure.

FIG. 2 is an enlarged view showing the hybrid drive device of thepresent disclosure.

FIG. 3 is an enlarged view showing the hybrid drive device of thepresent disclosure.

FIG. 4 is an enlarged view showing the hybrid drive device of thepresent disclosure.

FIG. 5 is a perspective view showing a main part of a cover thatconfigures the case of the rotary electric machine of the presentdisclosure.

MODES FOR CARRYING OUT THE DISCLOSURE

Next, embodiments for carrying out the disclosure of the presentdisclosure will be described with reference to the drawings.

FIG. 1 is a schematic configuration diagram showing a hybrid drivedevice 10 of the present disclosure. FIG. 2 and FIG. 3 are enlargedviews showing the hybrid drive device 10. The hybrid drive device 10 ismounted on a vehicle 1 and generates a driving force for traveling, andas shown in FIG. 1, includes an engine 11, a motor generator (rotaryelectric machine) MG, a first transmitting shaft 141 coupled to theengine 11, a second transmitting shaft 142 to which power is transmittedfrom the motor generator MG, a clutch K0 that couples the first andsecond transmitting shafts 141, 142 and that releases the connection ofthe two, and a power transmitting device 15. The hybrid drive device 10may be mounted on a rear-wheel drive vehicle as illustrated, may bemounted on a front-wheel drive vehicle, or may be mounted on afour-wheel drive vehicle including a transfer coupled to the powertransmitting device 15.

The engine 11 is an internal combustion engine that converts areciprocating motion of a piston (not shown) in accordance with thecombustion of a mixture of hydrocarbon fuel such as gasoline or lightoil and air into a rotational motion of a crankshaft (output shaft) 12.The crankshaft 12 of the engine 11 is coupled to the first transmittingshaft 141 via an annular coupling member 123 and a damper mechanism 13.For example, the damper mechanism 13 includes an input element coupledto the crankshaft 12 via the coupling member 123, an output elementcoupled to the first transmitting shaft 141, and a plurality of coilsprings (elastic bodies) that transmits a torque between the inputelement and the output element and that dampens a torsional vibration.

The motor generator MG is a synchronous generator motor (three-phasealternating current motor), and transmits and receives electric power toand from a power storage device (battery, not shown) via an inverterthat is not shown. The motor generator MG operates as an electric motorthat is driven by electric power from the power storage device togenerate a drive torque, and outputs a regenerative braking torque whenthe vehicle 1 is braked. The motor generator MG also operates as agenerator that generates electric power by using at least a part of thepower from the engine 11 that is operated under load.

As shown in FIGS. 1 to 3, the motor generator MG includes a stator 20and a rotor 30 housed in a motor case 8. The motor case 8 includes ahousing 80 having one end open and a cover 88 fixed to the housing 80 soas to cover the one end. The housing 80 of the motor case 8 is agenerally bottomed tubular body in which one end in the axial direction,that is, an end portion on the engine 11 side is opened, and the otherend in the axial direction, that is, an end portion on the powertransmitting device 15 side is closed. In the present embodiment, thehousing 80 is formed by casting an aluminum alloy, and includes atubular outer shell portion 81 and an end wall (wall portion) 82 thatcloses the other end of the outer shell portion 81.

As shown in FIG. 3, a front side flange portion 81 f having a pluralityof bolt holes is formed on one end (front end) of the outer shellportion 81 of the housing 80, that is, on an outer periphery on an openend side. The front side flange portion 81 f is fastened (fixed) to anengine block of the engine 11 via a plurality of bolts that is not shownand that is each inserted into a corresponding bolt hole. Further, theother end portion of the outer shell portion 81 protrudes from the endwall 82 toward the opposite side from the front side flange portion 81f, and a rear side flange portion 81 r having a plurality of bolt holesis formed on an outer periphery of the other end (rear end) of the outershell portion 81. The rear side flange portion 81 r is fastened (fixed)to an end portion (front end) of a transmission case 150 (see FIG. 1) ofthe power transmitting device 15 via a plurality of bolts that is notshown and that is each inserted into the corresponding bolt hole.

Further, a tubular shaft support portion 85 having a through hole isprovided in a center portion of the end wall 82 of the housing 80, andthe second transmitting shaft 142 protrudes from the through hole of thetubular support portion 85 toward the power transmitting device 15 side.The shaft support portion 85 may be formed integrally with the end wall82, or the shaft support portion 85 separate from the housing 80 may befixed to the end wall 82. A flange portion 142 f (see FIG. 2) is formedon an end portion of the second transmitting shaft 142 protruding fromthe end wall 82, and an inner peripheral portion of a flex plate 145 isfastened (fixed) to the flange portion 142 f via a plurality of boltsnot shown. Further, a seal member 90 is disposed in a clearance betweenthe second transmitting shaft 142 and the shaft support portion 85.

The cover 88 of the motor case 8 is a disk-shaped member formed bycasting an aluminum alloy. As shown in FIG. 3, the cover 88 includes aflange portion 88 f having a plurality of bolt holes arranged atintervals along the outer periphery, a through hole through which thefirst transmitting shaft 141 is inserted, and a plurality of bossportions 88 b each having a screw hole and that is formed at intervalsin the circumferential direction. A seal member 91 is disposed in aclearance between the cover 88 and the first transmitting shaft 141inserted through the through hole of the cover 88.

As shown in FIG. 3, the stator 20 includes an annular stator core 21 anda stator coil 22 wound around the stator core 21. The stator core 21 isintegrally formed by stacking a plurality of electromagnetic steelplates formed in an annular shape by press working and coupling theplurality of electromagnetic steel plates in a stacking direction, forexample. A plurality of bolt holes extending in the axial direction isformed in the stator core 21, and a bolt 87 is inserted into each bolthole. Each bolt 87 is screwed into the screw hole of the correspondingboss portion 88 b of the cover 88 and thus, the stator 20 is fixed tothe cover 88.

The cover 88 to which the stator 20 is fixed is fixed to the housing 80via a plurality of bolts 89 so that the stator 20 is surrounded by theouter shell portion 81 and a coil end 22 b faces the end wall 82. As aresult, the stator 20 is non-rotatably fixed to the motor case 8, andthe cover 88 forms an end wall portion of the motor case 8 extending inthe radial direction so as to face the motor generator MG and the clutchK0 on the engine 11 side. Further, in the present embodiment, as shownin FIG. 3, the cover 88 is fixed to the housing 80 so as to be close tothe front side flange portion 81 f, that is, a fastening portion (fixingportion) between the housing 80 and the engine block. This makes itpossible to fix the cover 88 and the stator 20 to the engine block andthe housing 80 more firmly.

The stator coil 22 includes three coils of a U phase, a V phase and a Wphase, and includes a coil end 22 a protruding from an end surface onthe damper mechanism 13 side (left side in FIG. 3) in the axialdirection of the stator core 21, and a coil end 22 b protruding from anend surface on the power transmitting device 15 side (right side in FIG.3). One end portion of the U phase, V phase, and W phase coils protrudesin the axial direction from the coil end 22 b and is used as a terminal22 c of each phase. The terminal 22 c of each phase is electricallycoupled to an inverter (not shown) via a bus bar (not shown) of the Vphase, the U phase, or the W phase corresponding to each terminal 22 c.

As shown in FIG. 3, the rotor 30 includes a rotor core 31, end plates32, 33 disposed on both sides of the rotor core 31 in the axialdirection, and a rotor support member 40 for holding the rotor core 31and the like. The rotor core 31 is formed by stacking a plurality ofelectromagnetic steel plates formed in an annular shape by pressworking, for example. Further, a plurality of through holes (not shown)each extending in the axial direction at intervals in thecircumferential direction is formed in the rotor core 31, and apermanent magnet is embedded in each through hole.

The rotor support member 40 includes an annular outer side half portion41, an annular inner side half portion 45 fixed to the outer side halfportion 41, and an annular plate member (annular member) 50. Both theouter side half portion 41 and the inner side half portion 45 are formedby machining a forged body made of a steel material (made of an ironalloy), for example. The plate member 50 is also made of steel material.As shown in FIG. 3, the outer side half portion 41 includes acylindrical outer tubular portion (tubular support portion) 42 in whichthe rotor core 31 is fixed to an outer peripheral portion, an annularflange portion 43 extended radially outward from one end (left end inFIG. 3) of the outer tubular portion 42 in the axial direction, and anannular radial protruding portion 44 protruding radially inward alongthe entire circumference from the other end side (right end in FIG. 3)of the center portion of the outer tubular portion 42 in the axialdirection. The rotor core 31 is fixed to the outer tubular portion 42 ofthe rotor support member 40 by shrink fitting processing in a state inwhich the end plates 32, 33 are disposed on both sides in the axialdirection. Further, the end plate 33 positioned on the opposite side ofthe flange portion 43 is fixed to the outer tubular portion 42 byswaging or the like. However, the rotor core 31 may be fixed to theouter tubular portion 42 by press fitting.

The inner side half portion 45 includes: an annular wall portion 46extended in the radial direction; an inner tubular portion 47 that has atubular shape and that is extended from an inner peripheral portion ofthe annular wall portion 46 to one side (left side in FIG. 3) in theaxial direction; a cylindrical supported portion 48 extended from theannular wall portion 46 to the other side (right side in FIG. 3), on anouter radial side of the inner tubular portion 47; and a short tubularpiston support portion 49 extended from the annular wall portion 46 toone side in the axial direction, on an outer radial side of thesupported portion 48. In the present embodiment, on a surface on theopposite side of the annular wall portion 46 from the piston supportportion 49, at least one recess portion 46 a recessed to the pistonsupport portion 49 side (one side) is formed so as to at least partiallyoverlap with the piston support portion 49 when viewed in the axialdirection of the rotor 30. The recess portion 46 a is formed in theannular wall portion 46 in order to correct the imbalance of the entirerotor 30 after the rotor core 31 and the end plates 32, 33 are fixed tothe rotor support member 40.

As shown in FIG. 3, an outer periphery of the annular wall portion 46 isfixed to an inner periphery of the radial protruding portion 44 of theouter side half portion 41 by welding. Further, an outer peripheralportion of the plate member 50 is fastened to the flange portion 43 ofthe rotor support member 40 (outer side half portion 41) by a pluralityof bolts 43 b so as to face the annular wall portion 46 at a distance inthe axial direction. In the present embodiment, the plate member 50 isfixed to the flange portion 43 in a state in which a surface of theouter peripheral portion is in contact with an end surface (left sideend surface in FIG. 3) on the opposite side of the flange portion 43from the rotor 30 side. Further, an axial protruding portion 43 p thathas a short cylindrical (annular) shape is formed in the flange portion43 so as to protrude in the axial direction from an outer peripheralportion of the end surface, with which the plate member 50 is incontact, to the opposite side (engine 11 side) from the rotor core 31side. As a result, the outer peripheral surface of the plate member 50is supported in the radial direction by the axial protruding portion 43p of the flange portion 43. A plurality of the axial protruding portions43 p may be formed on the outer peripheral portion of the end surface ofthe flange portion 43 at intervals in the circumferential direction.

Further, an outer peripheral surface of the supported portion 48 of therotor support member 40 (inner side half portion 45) is supported in theradial direction and is supported so as to be rotatable by the motorcase 8 via a radial bearing Brr (ball bearing in the present embodiment)held by the end wall 82 of the housing 80. The movement of the rotorsupport member 40 toward a speed change mechanism 17 side is restrictedby the housing 80, that is, the case 8 via the radial bearing Brr. Incontrast, the inner peripheral portion of the plate member 50 issupported in the radial direction and is supported so as to be rotatableby the cover 88 of the motor case 8 via a radial bearing Brf (an outerside radial bearing, in the present embodiment, a ball bearing). As aresult, the rotor 30 is supported in the radial direction by the motorcase 8 via the radial bearing Brf. Further, the inner tubular portion 47of the rotor support member 40 includes a spline formed on an innerperipheral surface of a tip end portion (an end portion on the engine 11side), and is always coupled (fixed) to the second transmitting shaft142 via the spline.

The clutch K0 couples the first transmitting shaft 141, that is, thecrankshaft 12 of the engine 11, and the second transmitting shaft 142,that is, the rotor 30 of the motor generator MG, and releases theconnection of the two. In the present embodiment, the clutch K0 is amulti-plate friction type hydraulic clutch that uses the rotor supportmember 40 of the rotor 30 that is always coupled to the secondtransmitting shaft 142 as a clutch drum, and is disposed in the motorcase 8, that is, on the inner radial side of the rotor 30. As shown inFIG. 3, in addition to the rotor support member 40 serving as a clutchdrum, the clutch K0 includes a clutch hub 61 that is disposed betweenthe annular wall portion 46 of the rotor support member 40 and the platemember 50 in the axial direction and that is always coupled (fixed) tothe first transmitting shaft 141, a plurality of friction plates (secondfriction engagement plates) 63, a plurality of separator plates (firstfriction engagement plates) 64 and backing plates 65 that arealternately arranged with the friction plates 63, a snap ring 66, apiston 67, a plurality of return springs SP, and a cancel plate (canceloil chamber defining member) 68.

As shown in FIG. 3, the clutch hub 61 includes a tubular portion 61 aand an annular wall portion 61 b extended radially inward from one endof the tubular portion 61 a. Splines 61 s are formed on an outerperipheral surface of the tubular portion 61 a, and an inner peripheryof the annular wall portion 61 b is fixed to the first transmittingshaft 141. Further, splines 42 s are formed on the inner peripheralsurface of the outer tubular portion 42 of the rotor support member 40serving as the clutch drum so as to be positioned closer to the flangeportion 43 side than the radial protruding portion 44.

The friction plate 63 is an annular member to which a friction materialis attached to both surfaces, and an outer peripheral portion of eachfriction plate 63 is fitted to the splines 42 s (inner peripheralportion) of the outer tubular portion 42. Further, the backing plate 65is fitted to the splines 42 s of the outer tubular portion 42 so as tobe able to come into contact with the friction plate 63 farthest fromthe piston 67 among the plurality of friction plates 63. The separatorplate 64 is an annular member in which both surfaces are formed to besmooth, and an inner peripheral portion of each separator plate 64 isfitted to the splines 61 s (outer peripheral portion) formed in thetubular portion 61 a of the clutch hub 61.

Further, an annular recess portion 42 a that is recessed radiallyoutward is formed in the splines 42 s of the outer tubular portion 42.The snap ring 66 is attached (fitted) to the annular recess portion 42a, and the movement of the backing plate 65, etc. in the axial direction(the movement in a direction away from the piston 67) is restricted bythe snap ring 66. In the present embodiment, when viewed in the radialdirection of the rotor 30, the annular recess portion 42 a is formed inthe splines 42 s so as to overlap in the axial direction with a part ofthe flange portion 43 (including the annular plate disposed between theflange portion 43 and the end plate 32), more specifically, an endsurface (an end surface in contact with the end plate 32) on the rotor30 side of the flange portion 43.

That is, in the present embodiment, the flange portion 43 is extendedradially outward from one end in the axial direction of the outertubular portion 42 of the rotor support member 40, and the radialprotruding portion 44 and the annular wall portion 46 are extendedradially inward from the other end side of the center portion in theaxial direction of the outer tubular portion 42. In such aconfiguration, when the rotor core 31 is fixed to the outer tubularportion 42 by shrink fitting processing or press fitting, according tothe experiments and analysis by the present inventors, it was found thata relatively large stress acts on the outer tubular portion 42 from therotor core 31 between the flange portion 43 and the radial protrudingportion 44 in the axial direction. Thus, when the annular recess portion42 a is formed between the flange portion 43 of the outer tubularportion 42 and the radial protruding portion 44 in the axial direction,the stress from the rotor core 31 is concentrated in the annular recessportion 42 a and there is a possibility that the durability of the outertubular portion 42 as well as the rotor support member 40 as a whole isdecreased. Based on this, in the present embodiment, the annular recessportion 42 a is formed in the outer tubular portion 42 so as to overlapwith a part of the flange portion 43 (the end surface on the rotor 30side) in the axial direction when viewed in the radial direction of therotor 30. As a result, it is possible to suppress the stress acting onthe outer tubular portion 42 from the rotor core 31 from beingconcentrated in the annular recess portion 42 a, and satisfactorilyensure the durability of the rotor support member 40.

Then, in the hybrid drive device 10, since the plate member 50 iscoupled to the flange portion 43 in a state in which the plate member 50is in contact with the end surface on the opposite side of the flangeportion 43 from the rotor 30 side, the annular recess portion 42 a canbe formed in the outer tubular portion 42 so as to overlap with at leasta part of the flange portion 43. In addition, when the plate member 50is fastened to the flange portion 43 by the bolt 43 b, since a thickness(axial length) of the flange portion 43 is ensured to some extent, it ispossible to further improve the durability of the rotor support member40 by making the end surface on the radial protruding portion 44 side ofthe annular recess portion 42 a substantially flush with the end surfaceon the rotor 30 side of the flange portion 43, when viewed in the radialdirection of the rotor 30.

The piston 67 includes an annular pressure receiving portion 67 a, atubular supported portion 67 b extended from an outer periphery of thepressure receiving portion 67 a to the clutch hub 61 side in the axialdirection, and a pressing portion 67 c formed radially outward of thesupported portion 67 b, and the piston 67 is disposed between theannular wall portion 46 of the rotor support member 40 and the platemember 50 in the axial direction. An inner peripheral surface of thepressure receiving portion 67 a of the piston 67 is supported so as tobe movable in the axial direction by an outer peripheral surface of theinner tubular portion 47 of the rotor support member 40 serving as aclutch drum via the seal member. Further, the outer peripheral surfaceof the pressure receiving portion 67 a is movably supported in the axialdirection by the inner peripheral surface of the piston support portion49 of the rotor support member 40 via a seal member, and an engagementoil chamber 69 a of the clutch K0 is defined between the annular wallportion 46 of the rotor support member 40 and the pressure receivingportion 67 a of the piston 67. Further, a plurality of recess portions(grooves) loosely fitted in the splines 42 s of the outer tubularportion 42 of the rotor support member 40 is formed in the outerperipheral portion of the pressing portion 67 c at intervals in thecircumferential direction. Thus, the piston 67 can be stopped fromrotating with respect to the outer tubular portion 42, and the piston 67and the outer tubular portion 42 can be rotated integrally.

The cancel plate 68 is an annular member disposed on an opposite side ofthe piston 67 from the annular wall portion 46 of the rotor supportmember 40. An inner peripheral portion of the cancel plate 68 is fixedto the inner tubular portion 47 of the rotor support member 40 by usinga snap ring. Further, an outer peripheral surface of the cancel plate 68movably supports an inner peripheral surface of the supported portion 67b of the piston 67 via a seal member, in the axial direction. As aresult, a centrifugal hydraulic pressure cancel chamber 69 b forcanceling a centrifugal hydraulic pressure generated in the engagementoil chamber 69 a is defined between the pressure receiving portion 67 aof the piston 67 and the cancel plate 68. Further, the plurality ofreturn springs (coil springs) SP is disposed at intervals in thecircumferential direction between the pressure receiving portion 67 a ofthe piston 67 and the cancel plate 68 in the axial direction. Eachreturn spring SP urges the piston 67 to a side away from the frictionplate 63 and the separator plate 64.

The power transmitting device 15 includes units such as a torqueconverter (fluid transmission device) 16 having a torque amplificationfunction, a lockup clutch CL, the speed change mechanism (automatictransmission) 17, a mechanical oil pump 18, and a hydraulic controldevice 19 that adjust working oil pressure, the transmission case 150that houses the speed change mechanism 17, etc. The torque converter 16includes a front cover serving as an input member that is always coupledto the second transmitting shaft 142 via the flex plate 145 (see FIGS. 1and 2), a pump impeller fixed to the front cover, and a turbine runnercoupled to an input shaft 17 i of the speed change mechanism 17, and astator that rectifies the flow of the working oil from the turbinerunner to the pump impeller so as to amplify the torque. However, thepower transmitting device 15 may include a fluid coupling that has nostator, instead of the torque converter 16. The lockup clutch CL couplesthe front cover and the input shaft 17 i of the speed change mechanism17 and releases the connection of the two.

The speed change mechanism 17 is, for example, a 4-speed to 10-speedtype multi-speed transmission including an output shaft 17 o, aplurality of planetary gears, a plurality of clutches and a plurality ofbrakes (engagement elements for shifting), in addition to the inputshaft 17 i. The speed change mechanism 17 shifts a power transmittedfrom at least one of the engine 11 and the motor generator MG to theinput shaft 17 i via the second transmitting shaft 142 and either one ofthe torque converter 16 and the lockup clutch CL, in a plurality ofstages, to output from the output shaft 17 o to left and right drivewheels DW via a differential gear DF. However, the speed changemechanism 17 may be a dual clutch transmission or a mechanicalcontinuously variable transmission. The torque converter 16 and thelockup clutch CL may be omitted from the power transmitting device 15.In this case, the speed change mechanism 17 may be coupled to the motorgenerator MG (the rotor support member 40 or the second transmittingshaft 142) via a clutch different from the clutch K0.

The oil pump 18 is a gear pump or a vane pump coupled to the pumpimpeller of the torque converter 16 via a winding transmittingmechanism, and is disposed on a shaft different from the input shaft 17i of the speed change mechanism 17. The oil pump 18 is driven by thepower from the second transmitting shaft 142 via the windingtransmitting mechanism, and sucks the working oil (ATF) stored in aworking oil storage portion (not shown) to pressure-feed to thehydraulic control device 19. The hydraulic control device 19 includes avalve body in which a plurality of oil passages is formed, a pluralityof regulator valves, a plurality of linear solenoid valves, and thelike. The hydraulic control device 19 adjusts the hydraulic pressure(working oil) from the oil pump 18 and supplies the hydraulic pressureto the torque converter 16, the lockup clutch CL, the clutches and thebrakes of the speed change mechanism 17. The transmission case 150 is acast product made of an aluminum alloy.

In addition, the hybrid drive device 10 includes a second hydrauliccontrol device 70 that supplies hydraulic pressure to the clutch K0. Thehydraulic control device 70 is attached to a lower portion of the motorcase 8 and adjusts the hydraulic pressure from the oil pump 18 to supplythe hydraulic pressure to the engagement oil chamber 69 a of the clutchK0 and the like. When the hydraulic pressure of the hydraulic controldevice 70 is supplied to the engagement oil chamber 69 a via a radialoil passage 83 formed in the housing 80 (shaft support portion 85) ofthe motor case 8, an axial oil passage L1 and a radial oil passage L3formed in the second transmitting shaft 142, and an oil hole 47 a formedin the inner tubular portion 47 of the rotor support member 40, thepiston 67 moves toward the cancel plate 68 by the action of anengagement hydraulic pressure. As a result, the separator plate 64 andthe friction plate 63 are pressed by the pressing portion 67 c and arefrictionally engaged, and the clutch K0 is engaged. Further, the workingoil drained from the hydraulic control device 70 is supplied to thecentrifugal hydraulic pressure cancel chamber 69 b of the clutch K0 viaa radial oil passage 84 formed in the end wall 82 (shaft support portion85), the axial oil passage L2 and a radial oil passage L4 formed in thesecond transmitting shaft 142, and the oil hole 47 a formed in the innertubular portion 47 of the rotor support member 40 so as to be side byside with an oil hole 47 b in the axial direction. The hydraulic controldevice 70 may be omitted from the hybrid drive device 10, and in thiscase, the clutch K0 may be supplied with the hydraulic pressure from thehydraulic control device 19 of the power transmitting device 15.Further, the centrifugal hydraulic pressure cancel chamber 69 b may beomitted from the clutch K0.

Subsequently, with reference to FIG. 4, support structures of the firstand second transmitting shafts 141, 142 and the rotor support member 40in the hybrid drive device 10, etc. will be described in detail.

As shown in FIG. 4, the first transmitting shaft 141 includes a firstend portion 141 a on the engine 11 side (left side in FIG. 4), a secondend portion 141 b on the speed change mechanism 17 side (right side inFIG. 4), and a disc-shaped expanded radius portion 141 e formed betweenthe first and second end portions 141 a, 141 b in the axial direction.The first end portion 141 a has an outer peripheral surface havingcolumnar surface shape, and the second end portion 141 b is formed in acylindrical shape (tubular shape) having a radius smaller than that ofthe first end portion 141 a, as illustrated. The expanded radius portion141 e of the first transmitting shaft 141 is formed to have a largerradius than that of the first and second end portions 141 a, 141 b, andis adjacent to the second end portion 141 b on the engine 11 side. Thatis, the second end portion 141 b protrudes from an end surface of theexpanded radius portion 141 e on the speed change mechanism 17 side tothe opposite side of the first end portion 141 a.

Further, an annular flange portion 141 f is extended from the expandedradius portion 141 e of the first transmitting shaft 141. The flangeportion 141 f is extended radially outward and toward the speed changemechanism 17 side, from the outer peripheral portion of the expandedradius portion 141 e so as to surround a part (about half of theexpanded radius portion 141 e side) of the second end portion 141 b onthe speed change mechanism 17 side of the plate member 50 of the rotorsupport member 40. In the present embodiment, an inner peripheralportion of a surface of the flange portion 141 f on the speed changemechanism 17 side is formed in a conical surface shape so that a radiusdecreases from the speed change mechanism 17 side toward the engine 11side. The inner periphery of the annular wall portion 61 b of the clutchhub 61 is fixed to an outer peripheral portion of the flange portion 141f by welding. Further, a thrust bearing (outer side thrust bearing) Btmthat supports the first transmitting shaft 141 in the axial direction isdisposed between the flange portion 141 f and the inner peripheralportion of the plate member 50 facing the flange portion 141 f.

An end portion 142 a of the second transmitting shaft 142 on the engine11 side is formed in a cylindrical shape (tubular shape) having an outerradius smaller than an outer radius of the expanded radius portion 141 eof the first transmitting shaft 141 and an inner radius larger than anouter radius of the second end portion 141 b of the first transmittingshaft 141. An internal space of the end portion 142 a communicates withan axial oil passage L2 of the second transmitting shaft 142. Further,splines into which the splines of the inner tubular portion 47 of therotor support member 40 are fitted are formed on an outer peripheralsurface of the end portion 142 a.

The first end portion 141 a of the first transmitting shaft 141 issupported in the radial direction by the crankshaft 12 of the engine 11via the coupling member 123 that couples the crankshaft 12 and thedamper mechanism 13, and a radial bearing Br0 (a fourth radial bearing,a ball bearing in the present embodiment). Further, the expanded radiusportion 141 e of the first transmitting shaft 141 is supported in theradial direction, between the first and second end portions 141 a, 141 bin the axial direction, by the cover 88 that is an end wall portion ofthe motor case 8 on the engine 11 side via a radial bearing Br1 (a firstradial bearing or an inner side radial bearing). As shown in FIG. 4, thecover 88 includes a cylindrical first tubular portion 881 that protrudesfrom an inner periphery thereof toward the speed change mechanism 17side so as to define a through hole through which the first transmittingshaft 141 is inserted. The radial bearing Br1 is disposed between aninner peripheral surface of the first tubular portion 881 and an outerperipheral surface of the expanded radius portion 141 e of the firsttransmitting shaft 141 so as to be positioned on the speed changemechanism 17 side (right side in the figure) than the seal member 91described above. In the present embodiment, the radial bearing Br1 is acylindrical roller bearing including a cup that is press-fitted into thefirst tubular portion 881 of the cover 88.

The second end portion 141 b of the first transmitting shaft 141 isinserted into the end portion 142 a that is formed in a tubular shapeand that is on the engine 11 side of the second transmitting shaft 142,and a radial bearing Br2 (a second radial bearing or an intermediateradial bearing) that supports the second transmitting shaft 142 in theradial direction is disposed between the outer peripheral surface of thesecond end portion 141 b of the first transmitting shaft 141 and theinner peripheral surface of the end portion 142 a of the secondtransmitting shaft 142 (therebetween in the radial direction). In thepresent embodiment, the radial bearing Br2 is a cylindrical rollerbearing including a cup that is press-fitted into the end portion 142 aof the second transmitting shaft 142. As can be seen from FIG. 4, whenviewed in the radial direction, the radial bearing Br2 overlaps at leastpartially with the clutch hub 61 fixed to the outer peripheral portionof the flange portion 141 f of the first transmitting shaft 141, in theaxial direction.

Further, between the end surface on the engine 11 side of the secondtransmitting shaft 142, that is, an end surface of the end portion 142 aand the end surface on the speed change mechanism 17 side of theexpanded radius portion 141 e in the axial direction, a thrust bearing(inner side thrust bearing) Bt1 that supports the first and secondtransmitting shafts 141, 142 in the axial direction is disposed. In thepresent embodiment, a thrust bearing that includes a single cage isadopted as the thrust bearing Bt1 in order to ensure oil permeability.As illustrated, a clearance is formed between an inner peripheralportion of the flange portion 141 f of the first transmitting shaft 141and the end portion 142 a of the second transmitting shaft 142.

Further, as shown in FIG. 4, an internal space communicating with theaxial oil passage L2 is defined between the end surface of the secondend portion 141 b of the first transmitting shaft 141 and an inner endsurface in which the axial oil passage L2 in the end portion 142 a ofthe second transmitting shaft 142 opens. Further, the first transmittingshaft 141 includes a plurality of inner side oil holes (first oil holes)hi formed in the second end portion 141 b at intervals in thecircumferential direction, and a plurality of outer side oil holes(second oil holes) ho each formed at intervals in the circumferentialdirection so as to pass through a vicinity of a base end portion of theflange portion 141 f of the first transmitting shaft 141.

The plurality of inner side oil holes hi is each opened on an innerperipheral surface of the second end portion 141 b, is opened betweenthe radial bearing Br2 and the thrust bearing Bt1 on the outerperipheral surface of the second end portion 141 b and the thrustbearing Bt1 in the axial direction, and forms an oil passage with aninternal space that is opened at the end surface of the second endportion 141 b. In the present embodiment, each inner side oil hole hi isformed obliquely so as to approach the engine 11 from the outerperipheral surface toward the inner peripheral surface of the second endportion 141 b of the first transmitting shaft 141. This makes itpossible to form the plurality of inner side oil holes hi each passingthrough the second end portion 141 b without causing a drill bit tointerfere with the flange portion 141 f that surrounds a part of thesecond end portion 141 b. A plurality of outer side oil holes o isformed so as to at least partially overlap with the radial bearing Br1and the thrust bearing Bt1 in the axial direction when viewed in theradial direction, and is extended in the radial direction.

Then, the second transmitting shaft 142 is supported in the radialdirection by the shaft support portion 85 that is provided in thehousing 80 (end wall 82) of the motor case 8 on the speed changemechanism 17 side of the end portion 142 a via a radial bearing (thirdradial bearing) Br3. In the present embodiment, the radial bearing Br3is a cylindrical roller bearing including a cup that is press-fitted inthe shaft support portion 85 of the housing 80. Further, a thrustbearing Bt2 that supports the second transmitting shaft 142 in the axialdirection is disposed between the flange portion 142 f of the secondtransmitting shaft 142 and the end wall 82 of the housing 80 in theaxial direction. In the present embodiment, the thrust bearing Bt2includes two cages.

The shaft support portion 85 of the housing 80 is formed in the end wall82 so as to have an axial length of approximately half an axial lengthof a part (cylindrical part) of the second transmitting shaft 142excluding the flange portion 142 f. Further, the inner tubular portion47 of the rotor support member 40 is fitted to the second transmittingshaft 142 so as to be positioned closer to the engine 11 than the shaftsupport portion 85. Further, splines on the inner peripheral surface ofthe inner tubular portion 47 are fitted to splines formed on the outerperipheral surface of the end portion 142 a of the second transmittingshaft 142, and a snap ring that restricts the axial movement of theinner tubular portion 47, that is, the rotor support member 40 isattached to the end portion 142 a. As a result, the rotor support member40, that is, the rotor 30 of the motor generator MG is always coupled tothe second transmitting shaft 142, and a fixing portion (spline fittingportion) f (see dotted line in FIG. 4) of the inner tubular portion 47,that is, the rotor support member 40 and the second transmitting shaft142 is at least partially overlapped with the radial bearing Br2 in theaxial direction when seen in the radial direction.

Further, as shown in FIG. 4, the cover 88 of the motor case 8 includes acylindrical second tubular portion 882 protruding in the axial directiontoward the speed change mechanism 17 so as to surround the first tubularportion 881. The second tubular portion 882 has an inner radius largerthan an outer radius of the first tubular portion 881. Further, theplate member 50 of the rotor support member 40 includes a cylindricaltubular portion 51 that protrudes in the axial direction from the innerperiphery thereof toward the engine 11. The tubular portion 51 of theplate member 50 has an inner radius larger than the outer radius of thefirst tubular portion 881 of the cover 88 and has an outer radiussmaller than an inner radius of the second tubular portion 882.

An outer race of the radial bearing Brf (ball bearing) is press-fittedinto the second tubular portion 882 so as not to come into contact witha surface (inner side surface) of the cover 88 on the speed changemechanism 17 side, and the tubular portion 51 of the plate member 50 isfitted in an inner race of the radial bearing Brf. As a result, theradial bearing Brf is disposed between an outer peripheral surface ofthe tubular portion 51 of the plate member 50 and an inner peripheralsurface of the second tubular portion 882 of the cover 88, and the platemember 50 is supported by the cover 88 via the radial bearing Brf so asto be rotatable and is also supported in the radial direction. Further,since the outer race of the radial bearing Brf is press-fitted into thesecond tubular portion 882 and the tubular portion 51 is fitted into theinner race of the radial bearing Brf, the movement of the plate member50, that is, the rotor support member 40 to the engine 11 side isrestricted by the cover 88, that is, the case 8 via the radial bearingBrf.

As described above, the inner radius of the tubular portion 51 of theplate member 50 is larger than the outer radius of the first tubularportion 881 of the cover 88. Thus, as illustrated, an annular clearancea is formed between the outer peripheral surface of the first tubularportion 881 and the inner peripheral surface of the tubular portion 51of the plate member 50. Further, as shown in FIGS. 4 and 5, a pluralityof (for example, three in the present embodiment) oil holes h1 is formedin the first tubular portion 881 of the cover 88 at intervals in thecircumferential direction. Each oil hole h1 is opened on the outerperipheral surface of the first tubular portion 881 and is opened on theinner peripheral surface of the first tubular portion 881 between theradial bearing Br1 and the seal member 91 in the axial direction. Thatis, each oil hole h1 communicates with a space in the axial directionbetween the clearance a, the radial bearing Br1, and the seal member 91.

Further, an end surface of the first tubular portion 881 of the cover 88faces the flange portion 141 f of the first transmitting shaft 141 at adistance, and an annular clearance b that communicates with theclearance a is formed between the end surface of the first tubularportion 881 and the flange portion 141 f, as shown in FIG. 4. The aboveclearance b also communicates with an inner peripheral portion of thespace in which the thrust bearing Btm is disposed. In contrast, the endsurface of the second tubular portion 882 of the cover 88 faces theplate member 50 at a distance, and an annular clearance c is formedbetween the end surface of the second tubular portion 882 (and the endsurfaces of the inner race and outer race of the radial bearing Brf) andthe plate member 50.

Further, the second tubular portion 882 includes a plurality of (forexample, two in the present embodiment) oil grooves g and a plurality of(for example, two in the present embodiment) oil holes h2. The pluralityof oil grooves g is spaced at intervals in the circumferential directionon the inner peripheral surface of the second tubular portion 882 sothat at least one oil groove g is positioned on an upper side in themotor case 8 and at least one oil groove g is positioned on a lower sidein the motor case 8, and each communicates with the clearance c and aspace defined between an inner side surface of the cover 88 and theradial bearing Brf. As shown in FIGS. 4 and 5, the plurality of oilholes h2 is formed so that at least one oil hole h2 is positioned on theupper side in the motor case 8 and at least one oil hole h2 ispositioned on the lower side in the motor case 8, and each opens at theouter peripheral surface of the second tubular portion 882 and opens ata bottom surface (inner peripheral surface) of the corresponding oilgroove g.

Further, as shown in FIGS. 4 and 5, the cover 88 includes a pair of oilcollecting guides (protruding portions) 885 protruding from the innerside surface so as to be included in an upper side half region in themotor case 8. The pair of oil collecting guides 885 is formed on theinner side surface of the cover 88 so that the oil collecting guides 885are separated from each other (are opened to the left and right) fromthe vicinity of an uppermost portion of the second tubular portion 882in the motor case 8 toward an outer radial side. Further, as shown inFIG. 4, the base end portion of each oil collecting guide 885 protrudesto the vicinity of the end surface of the second tubular portion 882.Further, in the present embodiment, one oil hole h2 is disposed betweenthe base end portions of the pair of oil collecting guides 885.

In the hybrid drive device 10 configured as described above, the firsttransmitting shaft 141 coupled to the crankshaft 12 of the engine 11 issupported in the radial direction by the cover 88 of the motor case 8via the radial bearing (first radial bearing) Br1, between the first endportion 141 a on the engine 11 side and the second end portion 141 b onthe speed change mechanism 17 side in the axial direction. The secondend portion 141 b of the first transmitting shaft 141 is inserted intothe end portion 142 a that is formed in a tubular shape and that is onthe engine 11 side of the second transmitting shaft 142, and a radialbearing (a second radial bearing) Br2 that supports the secondtransmitting shaft 142 in the radial direction is disposed between theouter peripheral surface of the second end portion 141 b of the firsttransmitting shaft 141 and the inner peripheral surface of the endportion 142 a of the second transmitting shaft 142. Further, the secondtransmitting shaft 142 is supported in the radial direction by the shaftsupport portion 85 that is provided in the housing 80 of the motor case8 on the speed change mechanism 17 side of the end portion 142 a via aradial bearing (third radial bearing) Br3.

That is, the second transmitting shaft 142 is supported in the radialdirection by the motor case 8 (cover 88) via the radial bearing Br2, thefirst transmitting shaft 141, and the radial bearing Br1 on the engine11 side, and is supported in the radial direction by the shaft supportportion 85 of the motor case 8 (housing 80) via the radial bearing Br3on the speed change mechanism 17 side. As a result, it is possible tosatisfactorily suppress the shaft runout of the second transmittingshaft 142 that transmits power from the rotor 30 of the motor generatorMG to the speed change mechanism 17. Further, in the hybrid drive device10, since it is not necessary to extend the shaft support portion 85 ofthe motor case 8 to the engine 11 side so as to support the radialbearing Br2, the shaft support portion 85 can be shortened, and anothermember, that is, the rotor support member 40 (inner tubular portion 47)can be disposed in the surplus space made as a result of the shaftsupport portion 85 being shortened. As a result, it is possible toshorten the axial length of the hybrid drive device 10 while suppressinga shaft runout of the second transmitting shaft 142.

Further, in the hybrid drive device 10, the inner tubular portion 47 ofthe rotor support member 40 is fitted to the second transmitting shaft142 on the engine 11 side of the shaft support portion 85 of the motorcase 8, and the fixing portion f of the inner tubular portion 47 (rotorsupport member 40) and the second transmitting shaft 142 is at leastpartially overlapped in the axial direction with the radial bearing Br2when seen in the radial direction. As a result, the axial length of thehybrid drive device 10 can be further shortened by effectively utilizingthe surplus space made by shortening the shaft support portion 85 of themotor case 8.

Further, the first end portion 141 a of the first transmitting shaft 141is supported in the radial direction by the coupling member 123 thatcouples the crankshaft 12 of the engine 11 and the damper mechanism 13via the radial bearing (fourth radial bearing) Br0. The firsttransmitting shaft 141 includes the expanded radius portion 141 e havinga radius larger than that of the second end portion 141 b adjacent tothe second end portion 141 b on the engine 11 side, and the expandedradius portion 141 e is supported in the radial direction by the cover88 of the motor case 8 via the radial bearing Br1. This makes itpossible to support both the first and second transmitting shafts 141,142 so that a shaft runout does not occur for the two.

Further, in the hybrid drive device 10, the annular flange portion 141 fis extended radially outward from the expanded radius portion 141 e ofthe first transmitting shaft 141 so as to surround at least a part ofthe second end portion 141 b on the speed change mechanism 17 side. Theclutch hub 61 of the clutch K0 is fixed to the outer peripheral portionof the flange portion 141 f so as to at least partially overlap with theradial bearing Br2 in the axial direction when viewed in the radialdirection. As a result, it is possible to connect the first transmittingshaft 141 and the clutch hub 61 of the clutch K0 while shortening theaxial length of the hybrid drive device 10.

Further, the motor case 8 of the hybrid drive device 10 includes thecover 88 serving as the end wall portion extending so as to face themotor generator MG and the clutch K0 on the engine 11 side, and therotor support member 40 includes the plate member (annular member) 50that faces the cover 88. The cover 88 includes the first tubular portion881 that protrudes in the axial direction from the inner peripherytoward the speed change mechanism 17, and the second tubular portion 882that protrudes in the axial direction toward the speed change mechanism17 so as to surround the first tubular portion 881, and the plate member50 of the rotor support member 40 includes the tubular portion 51 thatprotrudes in the axial direction from the inner periphery toward theengine 11. Further, the radial bearing (inner side radial bearing) Br1for supporting the first transmitting shaft 141 in the radial directionis disposed between the first transmitting shaft 141 (expanded radiusportion 141 e) coupled to the crankshaft 12 of the engine 11 and theinner peripheral surface of the first tubular portion 881 of the cover88, and the clearance a is formed between the outer peripheral surfaceof the first tubular portion 881 and the inner peripheral surface of thetubular portion 51 of the plate member 50. Moreover, the radial bearing(outer side radial bearing) Brf for supporting the rotor support member40 in the radial direction is disposed between the outer peripheralsurface of the tubular portion 51 of the plate member 50 and the innerperipheral surface of the second tubular portion 882 of the cover 88.

As a result, even if the cup of the radial bearing Br1 is press-fittedinto the first tubular portion 881 of the cover 88 of the motor case 8and the first tubular portion 881 is deformed, since the clearance a isformed between the outer peripheral surface of the first tubular portion881 and the inner peripheral surface of the plate member 50 of thetubular portion 51, the deformation of the first tubular portion 881does not affect the tubular portion 51 of the plate member 50. Even ifdeflection of the first transmitting shaft 141 with respect to the shaftcenter occurs in accordance with the rotation of the engine 11, sincethe clearance a is formed between the outer peripheral surface of thefirst tubular portion 881 and the inner peripheral surface of thetubular portion 51 of the plate member 50, the deflection of the firsttransmitting shaft 141 does not affect the tubular portion 51 of theplate member 50. Thus, in the hybrid drive device 10, the rotor supportmember 40 can be appropriately supported by the cover 88, that is, thecase 8 via the radial bearing Brf, and the fluctuation of the clearancebetween the stator 20 and the rotor 30 can be satisfactorily suppressed.

Further, since the expanded radius portion 141 e of the firsttransmitting shaft 141 is supported in the radial direction by the cover88 of the motor case 8 via the radial bearing Br1, a torque fluctuationvibration (vibration) of the engine 11 transmitted to the firsttransmitting shaft 141 is no longer directly transmitted to the outerside radial bearing Brf. As a result, in the hybrid drive device 10, theload acting on the radial bearing Brf for supporting the rotor supportmember 40, that is, the rotor 30 of the motor generator MG so as to berotatable and for also supporting the rotor support member 40 in theradial direction can be decreased, the durability thereof can be furtherimproved, and the radial bearing Brf can be decreased in size (the costcan be decreased).

Further, the thrust bearing (inner side thrust bearing) Bt1 is disposedbetween the end surface on the speed change mechanism 17 side of theexpanded radius portion 141 e of the first transmitting shaft 141 andthe end surface on the engine 11 side of the second transmitting shaft142. Moreover, the flange portion 141 f extended from the expandedradius portion 141 e of the first transmitting shaft 141 faces the endsurface of the first tubular portion 881 of the cover 88 and the platemember 50 on the speed change mechanism 17 side, and the thrust bearing(outer side thrust bearing) Btm is disposed between the flange portion141 f and the inner peripheral portion (a back surface of the tubularportion 51) of the plate member 50. Further, the first transmittingshaft 141 includes the plurality of inner side oil holes (first oilholes) hi each opened on the outer peripheral surface of the second endportion 141 b between the radial bearing Br2 and the thrust bearing Bt1in the axial direction and on the inner peripheral surface of the secondend portion 141 b.

Further, the first transmitting shaft 141 includes the plurality ofouter side oil holes ho that at least partially overlaps with the radialbearing Br1 and the thrust bearing Bt1 in the axial direction whenviewed in the radial direction. The cover 88 includes the plurality ofoil holes h1 each opened on the outer peripheral surface of the firsttubular portion 881 and opened on the inner peripheral surface of thefirst tubular portion 881 between the radial bearing Br1 and the sealmember 91 in the axial direction. Further, the annular clearance bcommunicating with the clearance a is formed between the end surface ofthe first tubular portion 881 and the flange portion 141 f, and theannular clearance c is formed between the end surface of the secondtubular portion 882 and the plate member 50. In addition, the secondtubular portion 882 includes the plurality of oil grooves g and theplurality of oil holes (second oil holes) h2 as described above.

As a result, the working oil serving as a lubricating cooling mediumsupplied from the axial oil passage L2 of the second transmitting shaft142 into the second end portion 141 b of the first transmitting shaft141 can be supplied from the plurality of inner side oil holes hi to theradial bearing (intermediate radial bearing) Br2 and the thrust bearingBt1, and can be supplied to the clutch K0 (the friction plate 63, theseparator plate 64, etc.) on the outer radial side via the thrustbearing Bt1. Further, the working oil serving as the lubricating coolingmedium supplied to the clutch K0 side can be supplied to the rotor core31 and the coil ends 22 a, 22 b of the stator 20 via a plurality of oilholes 42 o formed in the outer tubular portion 42 of the rotor supportmember 40, a plurality of oil grooves 31 g formed in the rotor core 31,and the like.

Further, a part of the oil scattered from the inner side oil hole hitoward the rotor 30 side of the motor generator MG, that is, the coilend 22 a side of the stator 20, travels along the inner side surface ofthe cover 88 and flows into the clearance c and the oil holes h2 of thesecond tubular portion 882. Thus, in the hybrid drive device 10, a partof the working oil that has flowed out from the inner side oil holes hito the rotor 30 side can be supplied to the radial bearing Brf. As aresult, the radial bearing Br2, the thrust bearing Bt1, and the radialbearing Brf can be sufficiently lubricated and cooled, and thedurability of each bearing can be satisfactorily ensured. In addition,on the inner side surface of the cover 88, the pair of oil collectingguides 885 is formed so as to collect the oil scattered from above andguide the oil to the clearance c between the end surface of the secondtubular portion 882 and the plate member 50 and to the oil holes h2 ofthe second tubular portion 882. Thus, the amount of oil that isscattered from the inner side oil holes hi of the first transmittingshaft 141 to the rotor 30 side and that flows into the clearance cbetween the end surface of the second tubular portion 882 and the platemember 50 can be increased, and a sufficient amount of oil can besupplied to the radial bearing Brf. However, the oil holes h2 may beomitted from the second tubular portion 882.

Moreover, in the hybrid drive device 10, the working oil that has passedthrough the thrust bearing Bt1 can supplied from the plurality of outerside oil holes ho of the first transmitting shaft 141 to the radialbearing Br1, and a part of the oil that has flowed into the outer sideoil holes ho can be supplied to the thrust bearing Btm via the clearanceb between the end surface of the first tubular portion 881 and theflange portion 141 f of the first transmitting shaft 141. A part of theoil that has flowed into the outer oil holes ho is also supplied to theradial bearing Brf via the clearance a between the outer peripheralsurface of the first tubular portion 881 and the inner peripheralsurface of the tubular portion 51 of the plate member 50. Further, theworking oil moves from the upper side to the lower side via the oilholes h1 of the first tubular portion 881 (cover 88). As a result, theradial bearings Br1, Brf and the thrust bearing Btm can be sufficientlylubricated and cooled, and the durability of each bearing can besatisfactorily ensured.

Further, in the hybrid drive device 10, the plurality of inner side oilholes hi of the first transmitting shaft 141 is formed obliquely so asto approach the engine 11 from the outer peripheral surface toward theinner peripheral surface of the second end portion 141 b. As a result,the flange portion 141 f of the first transmitting shaft 141 can beformed so as to surround a part of the second end portion 141 b in orderto shorten the axial length of the hybrid drive device 10, the firsttransmitting shaft 141 and the clutch hub 61 of the clutch K0 can beconnected, and the inner side and the outer side of the second endportion 141 b can be communicated via the plurality of inner side oilholes hi.

Further, in the hybrid drive device 10, the rotor support member 40incudes the annular wall portion 46 that is supported in the radialdirection by the motor case 8 (housing 80) via the radial bearing Brr,and the plate member 50 that is supported in the radial direction by themotor case 8 (cover 88) via the radial bearing Brr. Further, the platemember 50 is coupled to the annular flange portion 43 extended radiallyoutward from one end of the outer tubular portion 42 of the rotorsupport member 40 in the axial direction so that the plate member 50rotates integrally with the rotor 30, and the plate member 50 faces theannular wall portion 46 at a distance in the axial direction. Further,the plate member 50 is coupled to the flange portion 43 in a state ofbeing in contact with the end surface on the opposite side of the flangeportion 43 from the rotor core 31 side, and the flange portion 43includes the axial protruding portion 43 p that protrudes in the axialdirection from the outer peripheral portion of the end surface in whichthe plate member 50 is in contact with to the opposite side of the rotorcore 31 side and that supports the outer peripheral surface of the platemember 50 in the radial direction.

As a result, the plate member 50 is accurately aligned with the shaftcenter of the engine 11 and the speed change mechanism 17 by the axialprotruding portion 43 p of the flange portion 43 and thus, the rotor 30of the motor generator MG can be accurately aligned with the axialcenter of the engine 11, and the like. Further, by bringing the platemember 50 into contact with the end surface on the opposite side of theflange portion 43 from the rotor side, the distance in the axialdirection between the plate member 50 and the annular wall portion 46,that is, a disposition space of the clutch K0 can be sufficientlyensured, and the friction plates 63 and the separator plates 64 of thenumber in accordance with a torque capacity required for the clutch K0can be disposed. As a result, in the hybrid drive device 10, it ispossible to sufficiently ensure the torque capacity of the clutch K0while accurately aligning the rotor 30 of the motor generator MG withrespect to the shaft centers of the engine 11 and the speed changemechanism 17.

Further, the clutch K0 includes the piston 67 that is disposed betweenthe annular wall portion 46 (and the radial protruding portion 44) andthe plate member 50 in the axial direction, and the engagement oilchamber 69 a of the clutch K0 is defined by the piston 67 and theannular wall portion 46 of the rotor support member 40. As a result,since a torque transmitting function and a pressure receiving functionwhen engaging the clutch K0 are gathered on the outer tubular portion 42and the annular wall portion 46 sides, the rigidity required for theplate member 50 can be reduced so as to reduce the cost. Further, theplate member 50 of the rotor support member 40 does not transmit torquewhen the clutch K0 is engaged. Thus, the plate member 50 does not needto be coupled to the flange portion 43 via splines, etc., and may becoupled to the flange portion 43 by a relatively small number of bolts43 b so that the plate member 50 rotates integrally with the rotor 30.

As described above, a hybrid drive device of the present disclosureincludes a rotary electric machine (MG) having a stator (20) and a rotor(30), a transmission (17) coupled to the rotary electric machine (MG), aclutch (K0) that couples an engine (11) and the rotary electric machine(MG) and that releases a connection of the two, and a case (8) forhousing the rotary electric machine (MG) and the clutch (K0), the hybriddrive device (10) including: a first transmitting shaft (141) coupled toan output shaft (12) of the engine (11); a second transmitting shaft(142) that transmits power from the rotor (30) of the rotary electricmachine (MG) to the transmission (17); and rotor support member (40)that supports the rotor (30) of the rotary electric machine (MG) andthat is fixed to the second transmitting shaft (142), in which theclutch (K0) includes a clutch hub (61) fixed to the first transmittingshaft (141) and uses the rotor support member (40) as a clutch drum, andthe case (8) includes an end wall portion (88) that is extended so as toface the rotary electric machine (MG) and the clutch (K0) on the engine(11) side, the rotor support member (40) includes an annular member (50)that is disposed so as to face the end wall portion (88) of the case(8), the end wall portion (88) includes a first tubular portion (881)that protrudes in the axial direction from an inner periphery toward thetransmission (17), and a second tubular portion (882) that protrudes inthe axial direction toward the transmission (17) so as to surround thefirst tubular portion (881), the annular member (50) includes a tubularportion (51) that protrudes in the axial direction from an innerperiphery toward the engine (11), an inner side radial bearing (Br1) isdisposed between the first transmitting shaft (141) and an innerperipheral surface of the first tubular portion (881) of the end wallportion (88), a clearance (a) is formed between an outer peripheralsurface of the first tubular portion (881) of the end wall portion (88)and an inner peripheral surface of the tubular portion (51) of theannular member (50), and an outer side radial bearing (Brf) is disposedbetween an outer peripheral surface of the tubular portion (51) of theannular member (50) and an inner peripheral surface of the secondtubular portion (882) of the end wall portion (88).

In the hybrid drive device of the present disclosure, the case includesthe end wall portion that is extended so as to face the rotary electricmachine and the clutch on the engine side, the rotor support memberincludes the annular member that faces the end wall portion of the case.The end wall portion of the case includes the first tubular portion thatprotrudes in the axial direction from the inner periphery toward thetransmission, and the second tubular portion that protrudes in the axialdirection toward the transmission so as to surround the first tubularportion, and the annular member described above includes the tubularportion that protrudes in the axial direction from the inner peripherytoward the engine. The inner side radial bearing that supports the firsttransmitting shaft in the radial direction is disposed between the firsttransmitting shaft that is coupled to the output shaft of the engine andthe inner peripheral surface of the first tubular portion of the endwall portion, the clearance is formed between the outer peripheralsurface of the first tubular portion and the inner peripheral surface ofthe tubular portion of the annular member. The outer side radial bearingfor supporting the rotor support member in the radial direction isdisposed between the outer peripheral surface of the tubular portion ofthe annular member and the inner peripheral surface of the secondtubular portion of the end wall portion. Thus, even if deflection of thefirst transmitting shaft with respect to the shaft center occurs inaccordance with the rotation of the engine, since the clearance isformed between the outer peripheral surface of the first tubular portionand the inner peripheral surface of the tubular portion of the annularmember, the deflection of the first transmitting shaft does not affectthe tubular portion of the annular member. Thus, in the hybrid drivedevice of the present disclosure, the rotor support member can beproperly supported by the case via the outer side radial bearing.Further, since the first transmitting shaft is supported in the radialdirection by the end wall portion of the case via the inner side radialbearing, a torque fluctuation (vibration) of the engine transmitted tothe first transmitting shaft is no longer directly transmitted to theouter side radial bearing. As a result, in the hybrid drive device ofthe present disclosure, the load acting on the outer side radial bearingfor supporting the rotor support member, that is, the rotor of therotary electric machine in the radial direction can be decreased, thedurability thereof can be further improved, and the outer side radialbearing can be decreased in size (the cost can be decreased).

Further, the first transmitting shaft (141) may be supported by theoutput shaft (12) via a bearing (Br0) on the engine (11) side.

Further, the inner side radial bearing (Br1) may be a roller bearing,the outer side radial bearing (Brf) may be a ball bearing, the rotorsupport member (40) may be supported in a radial direction by the case(8, 80) via another ball bearing (Brr) on the transmission (17) side,the movement of the rotor support member (40) to the engine (11) sidemay be restricted by the case (8, 88) via the outer side radial bearing(Brf), and the movement of the rotor support member (40) to thetransmission (17) side may be restricted by the case (8, 80) via theother ball bearing (Brr).

Further, the rotor support member (40, 47) may be always connected tothe second transmitting shaft via a spline (f), the second transmittingshaft (142) may be supported in the radial direction by a shaft supportportion (85) provided in the case (8, 80) on the transmission (17) sidevia a radial bearing (Br3), one of the first transmitting shaft (141)and the second transmitting shaft (142) may be inserted inside the otherone formed in a tubular shape, and an intermediate radial bearing (Br2)may be disposed between the first transmitting shaft (141) and thesecond transmitting shaft (142) in the radial direction.

Moreover, the clutch (K0) may include a clutch hub (61) fixed to thefirst transmitting shaft (141) and may use the rotor support member (40)as a clutch drum, and the clutch hub (61) may be disposed between anannular wall portion (46) of the rotor support member (40) facing theannular member (50) and the annular member (50) in the axial direction.

The first transmitting shaft (141) may include a first end portion (141a) on the engine side, a second end portion (141 b) that is on thetransmission (17) side and that is formed in a tubular shape, and anexpanded radius portion (141 e) that is adjacent to the second endportion (141 b) on the engine (11) side and that has a larger radiusthan a radius of the second end portion (141 b), a flange portion (1410that has an annular shape may be extended radially outward from theexpanded radius portion (141 e) of the first transmitting shaft (141) soas to face an end surface of the first tubular portion (881) of the endwall portion (88) and the annular member (50) on the transmission (17)side, the clutch hub (61) may be fixed to an outer peripheral portion ofthe flange portion (141 f), the second end portion (141 b) of the firsttransmitting shaft (141) may be inserted into an end portion (142 a)that is formed in a tubular shape and that is on the engine (11) side ofthe second transmitting shaft (142), the intermediate radial bearing(Br2) that supports the second transmitting shaft (142) in the radialdirection may be disposed between an outer peripheral surface of thesecond end portion (141 b) of the first transmitting shaft (141) and aninner peripheral surface of the end portion (142 a) of the secondtransmitting shaft (142), and an inner side thrust bearing (Bt1) may bedisposed between an end surface on the transmission (17) side of theexpanded radius portion (141 e) of the first transmitting shaft (141)and an end surface on the engine (11) side of the second transmittingshaft (142), and an outer side thrust bearing (Btm) may be disposedbetween the flange portion (141 f) of the first transmitting shaft (141)and an inner peripheral portion of the annular member (50).

Further, the first transmitting shaft (141) may include an oil passage(hi, ho) that opens on an end surface of the second end portion (141 b)and that opens between the intermediate radial bearing (Br2) and theinner side thrust bearing (Bt1) in the axial direction. As a result, theoil serving as the lubricating cooling medium supplied in the second endportion of the first transmitting shaft can be supplied to theintermediate radial bearing and the inner side thrust bearing, and canbe supplied to the clutch or the rotor and the stator of the rotaryelectric machine via the inner side thrust bearing. Further, the oilscattered on the rotor side of the rotary electric machine can besupplied to the outer side radial bearing. As a result, the intermediateradial bearing, the inner side thrust bearing, and the outer side radialbearing can be sufficiently lubricated and cooled, and the durability ofeach bearing can be satisfactorily ensured.

A seal member (91) may be disposed between an outer peripheral surfaceof the first transmitting shaft (141) and the inner peripheral surfaceof the first tubular portion (881) of the end wall portion (88) and alsoon the engine (11) side of the inner side radial bearing (Br1), thefirst transmitting shaft (141) may include a plurality of second oilholes (ho) that at least partially overlap with the inner side radialbearing (Br1) and the inner side thrust bearing (Bt1) in the axialdirection when viewed in the radial direction, the end wall portion (88)may include a plurality of oil holes (h1) each opened on the outerperipheral surface of the first tubular portion (881) and opened on theinner peripheral surface of the first tubular portion (881) between theinner side radial bearing (Br1) and the seal member (91) in the axialdirection, and clearance (b, c) may be formed between the end surface ofthe first tubular portion (881) of the end wall portion (88) and theflange portion (141 f) of the first transmitting shaft (141), andbetween an end surface of the second tubular portion (882) of the endwall portion (88) and the annular member (5).

As a result, the oil that has passed through the inner side thrustbearing can be supplied to the inner side radial bearing from the secondoil holes of the first transmitting shaft. Further, a part of the oilthat has flowed into the second oil holes can be supplied to the outerside thrust bearing via the clearance between the end surface of thefirst tubular portion and the flange portion of the first transmittingshaft. Moreover, a part of the oil that has flowed into the second oilholes can be supplied to the outer side radial bearing via the clearancebetween the outer peripheral surface of the first tubular portion andthe inner peripheral surface of the tubular portion of the annularmember. Further, the oil can flow from the upper side to the lower sidevia the oil holes in the end wall portion. As a result, the inner sideradial bearing, the outer side thrust bearing, and the outer side radialbearing can be sufficiently lubricated and cooled, and the durability ofeach bearing can be satisfactorily ensured.

Further, the end wall portion (88) of the case (8) may include a pair ofoil collecting guides (885) that protrudes from a surface on thetransmission (17) side so as to collect oil scattered from above andguide the oil to the clearance (c) between the end surface of the secondtubular portion (882) and the annular member (50). Thus, the amount ofoil that is scattered from first oil holes of the first transmittingshaft to the rotor side of the rotary electric machine and that flowsinto the clearance between the end surface of the second tubular portionand the annular member can be increased, and a sufficient amount of theoil can be supplied to the outer side radial bearing.

The flange portion (141 f) of the first transmitting shaft (141) may beformed so as to surround at least a part of the second end portion (141b) on the transmission (17) side of the annular member (50), and theplurality of first oil holes (hi) may be formed obliquely so as toapproach the engine (11) from the outer peripheral surface toward aninner peripheral surface of the second end portion (141 b) of the firsttransmitting shaft (141). As a result, the first transmitting shaft andthe clutch hub of the clutch can be connected, and the inner side andthe outer side of the second end portion of the first transmitting shaftcan be communicated via the plurality of first oil holes, while theaxial length of the hybrid drive device is shortened.

The case (8) may include a housing (80) in which one end in the axialdirection is open and the other end in the axial direction is closed,and a cover (8) that is fixed to the housing (80) so as to cover the oneend and that forms the end wall portion.

Further, it is understood that the disclosure of the present disclosureis not limited to the embodiments described above, and variousmodifications can be made within the scope of the extension of thepresent disclosure. Furthermore, the embodiment described above ismerely one specific form of the disclosure described in the SUMMARY OFTHE DISCLOSURE, and does not limit the elements of the disclosuredescribed in the SUMMARY OF THE DISCLOSURE.

INDUSTRIAL APPLICABILITY

The present disclosure can be used in the manufacturing industry ofhybrid drive devices and the like.

1. A hybrid drive device including a rotary electric machine having astator and a rotor, a transmission coupled to the rotary electricmachine, a clutch that couples an engine and the rotary electric machineand that releases a connection of the two, and a case for housing therotary electric machine and the clutch, the hybrid drive devicecomprising: a first transmitting shaft coupled to an output shaft of theengine; and a second transmitting shaft that transmits power from therotor of the rotary electric machine to the transmission; and a rotorsupport member that supports the rotor of the rotary electric machine,wherein the case includes an end wall portion that is extended so as toface the rotary electric machine and the clutch on the engine side, therotor support member includes an annular member that is disposed so asto face the end wall portion of the case, the end wall portion includesa first tubular portion that protrudes in an axial direction from aninner periphery toward the transmission, and a second tubular portionthat protrudes in the axial direction toward the transmission so as tosurround the first tubular portion, the annular member includes atubular portion that protrudes in the axial direction from an innerperiphery toward the engine, an inner side radial bearing is disposedbetween the first transmitting shaft and an inner peripheral surface ofthe first tubular portion of the end wall portion, a clearance is formedbetween an outer peripheral surface of the first tubular portion of theend wall portion and an inner peripheral surface of the tubular portionof the annular member, and an outer side radial bearing is disposedbetween an outer peripheral surface of the tubular portion of theannular member and an inner peripheral surface of the second tubularportion of the end wall portion.
 2. The hybrid drive device according toclaim 1, wherein the first transmitting shaft is supported by the outputshaft via a bearing on the engine side.
 3. The hybrid drive deviceaccording to claim 2, wherein the inner side radial bearing is a rollerbearing, the outer side radial bearing is a ball bearing, the rotorsupport member is supported in a radial direction by the case viaanother ball bearing on the transmission side, and movement of the rotorsupport member to the engine side is restricted by the case via theouter side radial bearing, and the movement of the rotor support memberto the transmission side is restricted by the case via the other ballbearing.
 4. The hybrid drive device according to claim 3, wherein therotor support member is always connected to the second transmittingshaft via a spline, the second transmitting shaft is supported in aradial direction by a shaft support portion provided in the case on thetransmission side via a radial bearing, one of the first transmittingshaft and the second transmitting shaft is inserted inside the other oneformed in a tubular shape, and an intermediate radial bearing isdisposed between the first transmitting shaft and the secondtransmitting shaft in the radial direction.
 5. The hybrid drive deviceaccording to claim 4, wherein the clutch includes a clutch hub fixed tothe first transmitting shaft and uses the rotor support member as aclutch drum, and the clutch hub is disposed between an annular wallportion of the rotor support member facing the annular member and theannular member in the axial direction.
 6. The hybrid drive deviceaccording to claim 5, wherein the first transmitting shaft includes afirst end portion on the engine side, a second end portion that isformed in a tubular shape and that is on the transmission side, and anexpanded radius portion that is adjacent to the second end portion onthe engine side and that has a larger radius than a radius of the secondend portion, a flange portion that has an annular shape is extendedradially outward from the expanded radius portion of the firsttransmitting shaft so as to face an end surface of the first tubularportion of the end wall portion and the annular member on thetransmission side, the clutch hub is fixed to an outer peripheralportion of the flange portion, the second end portion of the firsttransmitting shaft is inserted into an end portion that is formed in atubular shape and that is on the engine side of the second transmittingshaft, the intermediate radial bearing that supports the secondtransmitting shaft in the radial direction is disposed between an outerperipheral surface of the second end portion of the first transmittingshaft and an inner peripheral surface of the end portion of the secondtransmitting shaft, and an inner side thrust bearing is disposed betweenan end surface on the transmission side of the expanded radius portionof the first transmitting shaft and an end surface on the engine side ofthe second transmitting shaft, and an outer side thrust bearing isdisposed between the flange portion of the first transmitting shaft andan inner peripheral portion of the annular member.
 7. The hybrid drivedevice according to claim 6, wherein the first transmitting shaftincludes an oil passage that opens on an end surface of the second endportion and that opens between the intermediate radial bearing and theinner side thrust bearing in the axial direction.
 8. The hybrid drivedevice according to claim 7, wherein a seal member is disposed betweenan outer peripheral surface of the first transmitting shaft and theinner peripheral surface of the first tubular portion of the end wallportion and also on the engine side of the inner side radial bearing,the first transmitting shaft includes a plurality of second oil holesthat at least partially overlap with the inner side radial bearing andthe inner side thrust bearing in the axial direction when viewed in theradial direction, the end wall portion includes a plurality of oil holeseach opened on the outer peripheral surface of the first tubular portionand opened on the inner peripheral surface of the first tubular portionbetween the inner side radial bearing and the seal member in the axialdirection, and a clearance is formed between the end surface of thefirst tubular portion of the end wall portion and the flange portion ofthe first transmitting shaft, and between an end surface of the secondtubular portion of the end wall portion and the annular member.
 9. Thehybrid drive device according to claim 8, wherein the end wall portionof the case includes a pair of oil collecting guides that protrudes froma surface on the transmission side so as to collect oil scattered fromabove and guide the oil to the clearance between the end surface of thesecond tubular portion and the annular member.
 10. The hybrid drivedevice according to claim 9, wherein the flange portion of the firsttransmitting shaft is formed so as to surround at least a part of thesecond end portion on the transmission side of the annular member, andthe plurality of oil holes is formed obliquely so as to approach theengine from the outer peripheral surface toward an inner peripheralsurface of the second end portion of the first transmitting shaft. 11.The hybrid drive device according to claim 10, wherein the case includesa housing in which one end in the axial direction is open and the otherend in the axial direction is closed, and a cover that is fixed to thehousing so as to cover the one end and that forms the end wall portion.12. The hybrid drive device according to claim 1, wherein the inner sideradial bearing is a roller bearing, the outer side radial bearing is aball bearing, the rotor support member is supported in a radialdirection by the case via another ball bearing on the transmission side,and movement of the rotor support member to the engine side isrestricted by the case via the outer side radial bearing, and themovement of the rotor support member to the transmission side isrestricted by the case via the other ball bearing.
 13. The hybrid drivedevice according to claim 12, wherein the rotor support member is alwaysconnected to the second transmitting shaft via a spline, the secondtransmitting shaft is supported in a radial direction by a shaft supportportion provided in the case on the transmission side via a radialbearing, one of the first transmitting shaft and the second transmittingshaft is inserted inside the other one formed in a tubular shape, and anintermediate radial bearing is disposed between the first transmittingshaft and the second transmitting shaft in the radial direction.
 14. Thehybrid drive device according to claim 13, wherein the clutch includes aclutch hub fixed to the first transmitting shaft and uses the rotorsupport member as a clutch drum, and the clutch hub is disposed betweenan annular wall portion of the rotor support member facing the annularmember and the annular member in the axial direction.
 15. The hybriddrive device according to claim 14, wherein the first transmitting shaftincludes a first end portion on the engine side, a second end portionthat is formed in a tubular shape and that is on the transmission side,and an expanded radius portion that is adjacent to the second endportion on the engine side and that has a larger radius than a radius ofthe second end portion, a flange portion that has an annular shape isextended radially outward from the expanded radius portion of the firsttransmitting shaft so as to face an end surface of the first tubularportion of the end wall portion and the annular member on thetransmission side, the clutch hub is fixed to an outer peripheralportion of the flange portion, the second end portion of the firsttransmitting shaft is inserted into an end portion that is formed in atubular shape and that is on the engine side of the second transmittingshaft, the intermediate radial bearing that supports the secondtransmitting shaft in the radial direction is disposed between an outerperipheral surface of the second end portion of the first transmittingshaft and an inner peripheral surface of the end portion of the secondtransmitting shaft, and an inner side thrust bearing is disposed betweenan end surface on the transmission side of the expanded radius portionof the first transmitting shaft and an end surface on the engine side ofthe second transmitting shaft, and an outer side thrust bearing isdisposed between the flange portion of the first transmitting shaft andan inner peripheral portion of the annular member.
 16. The hybrid drivedevice according to claim 15, wherein the first transmitting shaftincludes an oil passage that opens on an end surface of the second endportion and that opens between the intermediate radial bearing and theinner side thrust bearing in the axial direction.
 17. The hybrid drivedevice according to claim 1, wherein the rotor support member is alwaysconnected to the second transmitting shaft via a spline, the secondtransmitting shaft is supported in a radial direction by a shaft supportportion provided in the case on the transmission side via a radialbearing, one of the first transmitting shaft and the second transmittingshaft is inserted inside the other one formed in a tubular shape, and anintermediate radial bearing is disposed between the first transmittingshaft and the second transmitting shaft in the radial direction.
 18. Thehybrid drive device according to claim 17, wherein the clutch includes aclutch hub fixed to the first transmitting shaft and uses the rotorsupport member as a clutch drum, and the clutch hub is disposed betweenan annular wall portion of the rotor support member facing the annularmember and the annular member in the axial direction.
 19. The hybriddrive device according to claim 18, wherein the first transmitting shaftincludes a first end portion on the engine side, a second end portionthat is formed in a tubular shape and that is on the transmission side,and an expanded radius portion that is adjacent to the second endportion on the engine side and that has a larger radius than a radius ofthe second end portion, a flange portion that has an annular shape isextended radially outward from the expanded radius portion of the firsttransmitting shaft so as to face an end surface of the first tubularportion of the end wall portion and the annular member on thetransmission side, the clutch hub is fixed to an outer peripheralportion of the flange portion, the second end portion of the firsttransmitting shaft is inserted into an end portion that is formed in atubular shape and that is on the engine side of the second transmittingshaft, the intermediate radial bearing that supports the secondtransmitting shaft in the radial direction is disposed between an outerperipheral surface of the second end portion of the first transmittingshaft and an inner peripheral surface of the end portion of the secondtransmitting shaft, and an inner side thrust bearing is disposed betweenan end surface on the transmission side of the expanded radius portionof the first transmitting shaft and an end surface on the engine side ofthe second transmitting shaft, and an outer side thrust bearing isdisposed between the flange portion of the first transmitting shaft andan inner peripheral portion of the annular member.
 20. The hybrid drivedevice according to claim 1, wherein the case includes a housing inwhich one end in the axial direction is open and the other end in theaxial direction is closed, and a cover that is fixed to the housing soas to cover the one end and that forms the end wall portion.